Hand-held power tool

ABSTRACT

A manual machine tool having a drive motor, a gearbox and a tool holder, wherein a motor output of the drive motor having a gearbox drive of the gearbox and a gearbox output of the gearbox are coupled to the tool holder in a manner which permits rotation, wherein the manual machine tool has an actuating device to adjust the gearbox between its switch positions, wherein the actuating device has an actuating part which is movably mounted between actuating positions relative to a machine housing of the manual machine tool and which can be manually actuated, which actuating part is coupled to the at least one switching gear element to set the switch positions. The actuating device has a locking arrangement with locking indentations arranged on a locking structure to lock the actuating part in the actuating positions, which locking indentations are assigned to actuating positions of the actuating part, and with a locking part to engage in the locking indentations.

This application claims priority based on an International Applicationfiled under the Patent Cooperation Treaty, PCT/EP2018/072318, filed Aug.17, 2018, which claims priority to DE 202017006789.7, filed Aug. 29,2017 and to DE 102018111792.2, filed May 16, 2018.

BACKGROUND OF THE INVENTION

The invention relates to a manual machine tool having a drive motor, agearbox and a tool holder, wherein a motor drive of the drive motorhaving a gearbox drive of the gearbox and a gearbox output of thegearbox which can be rotated about a rotational axis which are coupledto the tool holder in a manner which permits rotation, wherein themanual machine tool has an actuating device to adjust the gearboxbetween its switch positions in which speed ratios between the gearboxdrive and the gearbox output are different, wherein the actuating devicehas an actuating part which can be manually actuated by an operated ofthe manual machine tool and is movably mounted relative to a machinehousing of the manual machine tool between actuating positions assignedto the switch positions of the gearbox, which actuating part is coupledto the at least one switching gear element to set the switch positions,in particular by means of a coupling element.

A manual tool machine of this type is for example described in EP 1 886769 A1. The manual machine tool has a four-speed gearbox in whichswitching gear elements in the form of hollow wheels are switched bymeans of an actuating device. The actuating device has actuating ringswhich are connected to setting elements by means of cam guides, whichsetting elements in turn actuate the hollow wheels and therefore theswitching gear elements. The construction is complex. The operator mustadjust the actuating parts into the respective final positions toreliably adjust the gearbox into its final switch positions.

SUMMARY OF THE INVENTION

The object of the present invention is therefore to provide a manualmachine tool with an improved operating concept.

In order to achieve the object, in a manual machine tool of the typementioned at the outset there is a provision for the actuating device tohave a locking arrangement to lock the actuating part in the actuatingpositions with locking indentations arranged on a locking structure,which locking indentations are assigned to actuating positions on theactuating part, and for the locking structure to have a control surfacearrangement with gliding surfaces along which the locking part can glideand which extend from at least two locking indentations to a vertexarranged between the locking indentations and protruding in front of thelocking indentations, wherein the locking part has an unstable positionon the vertex such that the locking part is guided past the vertex intoone of the locking indentations adjacent to the vertex.

Several pairs of adjacent locking indentations can be provided, betweenwhich a vertex is arranged in each case.

The fundamental idea of this is that the locking part is guided as itwere past the vertex in the direction of a locking indentation arrangedadjacent to the vertex, in other words the locking part cannot remain onthe vertex but instead takes on an unstable position on the vertex. Thevertex is for example designed such that it prevents and/or is narrow toprevent the locking part from taking up a stable position on the vertex.

Starting from the vertex, the locking part advantageously reaches one ofthe locking indentations arranged adjacent to the vertex.

The locking arrangement enables an adjustment of the actuating part inthe manner of a toggle that only takes on a stable position in definedend positions or switch positions.

The vertex can also be called a tilting contour, in particular a tiltingline or a tilting point or an arrangement of tilting points. The lockingpart has an unstable position on the vertex or the tilting contour, inparticular the tilting point or the arrangement of tilting points or thetilting line and tilts or automatically moves from the vertex or thetilting contour into one of the locking indentations arranged adjacentto the vertex.

In order to achieve the object, in a manual machine tool of the typementioned at the outset in an alternative formulation, there is aprovision for the actuating device to have a locking arrangement to lockthe actuating part in the actuating positions with locking indentationsarranged on a locking structure, which locking indentations are assignedto actuating positions on the actuating part, and for the lockingstructure to have a control surface arrangement with gliding surfacesalong which the locking part can glide and which extend from at leasttwo locking indentations to a vertex or a tilting contour arrangedbetween the locking indentations and protruding in front of the lockingindentations, wherein the locking part has an unstable position on thevertex or the tilting contour such that the locking part is guided pastthe vertex or the tilting contour into one of the locking indentationsadjacent to the vertex or the tilting contour.

The locking part is advantageously guided past the vertex or the tiltingcontour automatically and/or automatically and/or without operationand/or by means of a spring force acting on the locking part into one ofthe locking indentations adjacent to the vertex or the tilting contour.

The vertex or the tilting contour is preferably a narrow line ordesigned as a narrow line or line-shaped.

A single vertex or a single tilting contour is preferably provided orarranged between two adjacent locking indentations.

The vertex or tilting contour is preferably designed as a type of burrand/or ridge and/or edge or formed by these. Only a single burr orvertex or ridge of this kind or a single edge of this kind is preferablyprovided between two locking indentations.

Two gliding surfaces with an inclination and/or with slopes in thedirection of the locking indentation arranged on the respective glidingsurface advantageously extend from the vertex in each case.

The gliding surfaces run to the vertex and intersect in the region ofthe vertex.

The actuating part can therefore be locked in a respective switchposition, for example in the respective longitudinal positions, inparticular longitudinal end positions, relative to an actuatinglongitudinal axis and/or a pivot position relative to an actuating pivotaxis of the actuating part.

The locking part is preferably sprung or elastic.

For example, a separate spring, in particular a coil spring, is providedto spring load the locking part. It is also possible, however, for thelocking part to be arranged on a spring arm or to have a spring arm,which in turn is arranged on a component which is locally fixed, forexample a component which is locally fixed relative to the machinehousing or the actuating part.

The locking structure is preferably fixed to prevent movement relativeto the actuating part. The locking structure is preferably arranged onthe actuating part.

It is advantageous if the control surface arrangement according to theinvention extends between the respective locking indentations or alllocking indentations of a locking arrangement or locking structure suchthat the locking part is as it were guided into one of the lockingindentations by force and takes on an unstable position on the verticesof the control surface arrangement.

The vertex is preferably straight or arch-shaped in full or in sections.It is understood that the vertex can overall be straight or overall bearch-shaped between two locking indentations or can also havearch-shaped or straight sections. A respective gliding surface extendsfrom the locking indentation to the assigned vertex along the entirelength of this.

The locking structure can have more than two locking indentations, forexample three or four locking indentations. It is possible for a vertexto only be provided between two locking indentations of this type, onwhich vertex the locking part takes on an unstable position. It ispreferable, however, for a vertex to be provided between several pairsor each pair of two locking indentations, on which vertex the lockingpart takes on an unstable position, such that it is guided into thelocking indentation arranged adjacent to the respective vertex.Consequently, a preferred embodiment provides for the locking structuresto have at least two or three locking indentations, between which avertex is arranged in each case, on which vertex the locking part has anunstable position and from which vertex a gliding surface extends out tothe respective locking indentation in each case. If for example threelocking indentations are provided, a total of three vertices areprovided, with two gliding surfaces extending from each to an assignedlocking indentation in each case.

It is preferable for the vertices to run in a star-shaped manner or tocross over one another or both. For example, a central vertex point canbe provided at which the vertices cross or from which the vertices runin a star-shaped manner and on which the locking part has an unstableposition. For example, an arrangement in the manner of a mountain peakwith side valleys extending away from the mountain peak is provided inwhich the locking part is guided in each case when it is unstable on thepeak of the mountain or on ridges which extend away from the peak or thevertex point.

The locking recesses expediently have the same angular distances fromone another. Of course angular distances that are different from oneanother are also possible. In particular, the angular distances betweenthe locking indentations correspond to the actuating positions of theactuating part.

It is preferable for the locking indentations to be arranged in cornerareas of a polygon. The polygon preferably has equal sides. There can,for example, be a provision for the locking indentations to be arrangedin the respective corner areas of a square or a rectangle. Lockingindentations can, however, also be arranged in corner areas of trianglesor pentagons or the like, between which vertices then extend on whichthe locking part has an unstable position.

Gliding surfaces which face one another are assigned to at least one ofthe locking indentations, between which gliding surfaces a depression orchannel is formed which extends from the locking indentation to thevertex. The depressions or channels can extend up to a crossing point orstar point of two or more vertices. An inner radius of the depression orchannel is preferably smaller than an outer radius of a gliding surfaceof the locking part provided to guide along the locking structure. Forexample, the depression or channel forms a guide, in particular a linearguide, which guides the locking part in the direction of the assignedlocking indentation.

The gliding surfaces which face one another are for example aligned inan approximately V shape.

The locking structure or the control surface arrangement preferably hasthe shape of a pyramid, for example a three-sided or four-sided pyramid,wherein depressions or channels are arranged on the side surfaces whichextend towards the top of the pyramid and each extend to a respectivelocking indentation. The base of the pyramid can for example have theouter circumference of a triangle, square, pentagon or other polygon.

A construction in which the locking part is actively actuated by anoperator in the direction of the vertex is possible.

It is preferred, however, for at least one of the gliding surfaces to bea sloped surface and/or a surface which is convex relative to thelocking part. A combination of sloped surface and convex surface iseasily possible. A convex surface can have equal or unequal radii. Thelocking part is guided in the direction of the locking indentation or inthe direction of a depression or channel between gliding surfaces whichface one another by the sloped surface or convex surface.

At least one of the gliding surface has an incline of at least 12degrees from the vertex to the locking indentation adjacent to thevertex. The incline is preferably steeper, for example 15 degrees or 20degrees. It is particularly preferable for the incline to be at least 25degrees or 30 degrees. A correspondingly stronger actuating force in thedirection of the locking indentation is achieved by a relatively steepincline or a steep angle of inclination of the gliding surface.Consequently, the actuating part can be spring loaded in the directionof one of the actuating positions with greater force.

The locking structure preferably has several gliding surfaces, one ofwhich gliding surfaces has a twisting of the locking structure and thelocking part relative to one another and the other of which glidingstructures has a linear arrangement of the locking structure and thelocking part relative to one another.

A gliding surface along which the locking part glides in the event of arelative twisting of the locking structure and the locking partexpediently has a more gentle incline or a more gentle angle ofinclination than a gliding surface along which the locking part glidesin the event of a linear arrangement of the locking structures of thelocking part relative to one another. A rotational movement is generallyeasier than a sliding movement. As a result of the steep incline or thesteep angle of inclination of the gliding surface assigned to the lineararrangement of locking structure and locking part, a sufficiently largeactuating force is exerted on the actuating element in the direction ofthe actuating position assigned to the linear arrangement even in thecase of a linear arrangement.

The locking part can for example have a gliding surface that runs to apeak in order to glide along the locking structure. It is preferable,however, for the locking part to have a convex and/or spherical glidingsurface to glide along the locking structure. The spherical or convexgliding surface glides particularly easily along the locking structure.A convex or spherical gliding surface is particularly unstable in theregion of the vertex or vertices.

In order to improve the gliding properties of the locking part, thegliding surface of this can have a gliding coating, for example made ofpolytetrafluoroethylene, a ceramics material or the like.

It is advantageous if the locking part is spring loaded in the directionof the locking indentations or in the direction of a locking positionwhich engages in the locking indentations.

For example, the locking part can be arranged on a spring arm or canhave a spring arm.

The locking part is preferably spring loaded by means of a springarrangement or a spring in the direction of the locking indentations, inparticular a locking spring, a leaf spring or the like.

The locking part is advantageously guided into one of the lockingindentations adjacent to the vertex due to the unstable position on thevertex as a result of the spring loading, in particular the springloading of the at least one spring or a spring arrangement. The lockingpart glides along the gliding surfaces in the direction of one of thelocking indentations in each case starting from the vertex as a resultof the spring loading.

The fact that the locking structure or control surface arrangement has alower friction coefficient in the region of at least one vertex,preferably in the region of all the vertices, than on a surfaceextending away from the vertex, for example one of the gliding surfacesand/or in the region of the locking indentations can also contribute tothe possible unstable position of the locking part in the region of thevertex or the vertices. The friction coefficient can be lower in theregion of the locking indentations than in the region of the vertexrunning adjacent to the locking indentation or the vertices runningadjacent to the locking indentation. However, with respect to thegliding surfaces it is also advantageous if they have a lower frictioncoefficient, or in any case a lower friction coefficient than arespective locking indentation adjacent to which the gliding surfaceruns or to which the gliding surface is assigned.

The friction properties in the region of the at least one vertex can forexample be achieved by means of a gliding coating on a base body of thelocking structure, for example by means of polytetrafluoroethylene,ceramics material or another material with a low level of friction ofthe like.

It is also possible for composite materials, for example, to be used forthe locking structure or control surface arrangement. Sections of amaterial component of the composite material with lower levels offriction can be provided in the region of the vertex or the protrudingsections of the locking structure or control surface arrangement whileadjacent to these sections another material component of the compositematerial with a higher level of friction than in the region of the atleast one vertex is provided.

The locking structure and the locking part can for example have pairs ofmaterials which glide well relative to one another, for example steeland steel sprayed with plastic or pairs of plastic and metal.Furthermore, the surfaces of the locking structure and locking partwhich glide along one another can comprise different metals, inparticular pairs of steel and bronze or steel and grey cast iron.

It is further advantageous if the locking part and/or the lockingstructure comprises polyimide, polyamide or polyoxymethylene (POM) inthe region of the surfaces that glide along one another.

The locking arrangement is preferably arranged in a hidden manner. Thelocking arrangement is preferably arranged on a lower side of theactuating part and/or between the actuating part and the gearboxhousing, in particular a cover of the gearbox housing.

The locking part is preferably supported and/or movably mounted on thegearbox housing or the cover of this. The locking structure ispreferably arranged on the actuating part, for example on the inner sideor lower side which faces the gearbox or gearbox housing.

The locking part can, however, also be arranged on the actuating partwhich is movable relative to the machine housing. The locking structureis then fixed in a location relative to the machine housing or gearboxhousing.

Two or more locking recesses can be provided on the locking structure inwhich locking recesses the locking part is arranged.

An actuating handle is preferably arranged on the actuating part formanual actuation. The actuating part can also, however, be coupled to anactuating handle which can be manually actuated in a manner whichenables movement or connected to it in a fixed manner.

It is understood that several switching gear elements which can beactuated or switched by the actuating device and/or several couplingelements to couple a respective switching gear element to the actuatingdevice can be provided.

It is preferable for a switching gear element to be coupled to theactuating part by means of a coupling element. It is also possible for aswitching gear element to form a coupling element to couple a furtherswitching gear element to the actuating part or the actuating device.

The coupling element assigned to a switching gear element can form apart of the switching gear element or be connected to the switching gearelement in a fixed manner.

It is preferable for the coupling element assigned to the switching gearelement to be movable relative to the switching gear element, forexample able to be slid and/or pivoted.

The actuating part is expediently pivotably mounted relative to themachine housing of the manual machine tool about an actuating pivot axisand/or displaceably mounted about a linear actuating longitudinal axis.It is possible that the abilities to move, namely the ability to pivotand the ability to adjust in a linear manner enable the actuating partto make overlapping movements. It is further possible that the actuatingpart has just one degree of freedom of movement when pivoting or severaldegrees of freedom of movement when pivoting. The actuating part canalso have just one degree of linear freedom of movement or several, forexample two, degrees of linear freedom of movement.

The actuating part can be mounted on the machine housing or on thegearbox housing along the actuating linear axis in a manner which enablelinear displacement and/or in a manner which enables pivoting about anactuating pivot axis.

A spring arrangement is expediently arranged between the actuating partand the at least one switching gear element. It is preferable for aspring arrangement or a part of this to be arranged between eachswitching gear element and the actuating part. The spring arrangementplaces a load on the switching gear element in its respective settingposition or a setting position assigned to the position of the actuatingpart during and/or after an actuation of the actuating part. If theswitching gear element cannot reach its setting position, for examplebecause its teeth are not aligned with the teeth of a gear wheel thatworks with the switching gear element, the spring loading ensures thatin the event of a relative rotational adjustment of the switching gearelement and gear wheel, the two components can mesh together in apositive-locking manner.

At least one coupling element can be provided to supply at least part ofthe spring arrangement or the spring arrangement as a whole.

The coupling element expediently comprises a spring bow or is formed bya spring bow. The spring box expediently extends in a ring-shaped manneraround the respective switching gear element. The spring bow can forexample have bow arms, which are elastic and flexible. The longitudinalends of the spring bow expediently engage in corresponding recesses, forexample bores, grooves, guides, in particular longitudinal guides or thelike, on the respective switching gear element.

There is preferably a provision for the switching gear element to have afirst switching gear element and a second switching gear element, whichcan be adjusted between a first setting position and a second settingposition in each case in a linear manner relative to a gearbox housingusing the actuating device. It is possible for the respective switchinggear element to be able to be adjusted in a linear manner by means of alinear adjustment of the actuating part.

A deflection of a movement of the actuating part into a movement of therespective switching gear element is, however, also easily possible.There can advantageously be a provision for the first switching elementto be able to be adjusted by a pivoting movement of the actuating partabout the actuating pivot axis in a linear manner along its setting axisby means of a deflecting gear.

An advantageous embodiment provides for the deflecting gear to comprisea carrier ring which extends in a ring-shaped manner around the gearboxhousing and is mounted such that it is rotatable about the actuatingpivot axis, which carrier ring is coupled to the first switching gearelement by means of a first coupling element to enable the linearadjustment of this.

It is preferably if the actuating part is displaceably mounted on thecarrier ring in a linear manner along an actuating longitudinal axis andcoupled to the at least second switching gear element using a secondcoupling element to achieve linear displacement of the second switchinggear element. The fundamental idea of this is that in principle thecarrier ring forms a rotating body or a pivot bearing for the actuatingpart. The actuating part can therefore pivot about the gearbox housingwith the carrier ring in order to switch the first switching gearelement. In turn, the actuating part is displaceably mounted in a linearmanner on this carrier ring, such that it can carry out the linearmovement to adjust the second switching gear element directly. A furtherslide or support for the actuating part or the second coupling elementis not necessary. It is also possible in this arrangement to carry outthe two actuating movements, namely about the actuating longitudinalaxis and actuating pivot axis, which can occur in parallel to oneanother, in an overlaid manner such that the first switching gearelement and the second witching gear element can be switchedsimultaneously and the gearbox can be switched for example from a firstswitch position or a first gear directly into a third gear or a thirdswitch position without the second or an intermediate switch position ora gear arranged in between needing to be controlled.

A spring arrangement is expediently arranged between the actuating partand the first switching gear element or the second switching gearelement or both. The spring arrangement between the second switchinggear element and the actuating part can in particular be provided by thesecond coupling element, for example exclusively by the second couplingelement. It is also possible, however, for a spring or springarrangement which is separate to this to be provided. A springarrangement and the elastic coupling element can also be provided. Thespring arrangement can however easily be provided between the firstswitching gear element and the actuating part by the first couplingelement.

The first coupling element or the second coupling element or both canfor example comprise or be a spring element. In particular, a spring bowor the like is suitable as an elastic, flexible coupling element.

A preferred and simple embodiment provides for the actuating part to becoupled to the second switching gear element exclusively by means of thesecond coupling element or by means of a single component. Consequentlyno further component is necessary between the switching gear element andthe actuating part. In particular, the spring bow which has already beenmentioned is suitable as a second coupling element and extends as asingle component to make the connection between the actuating part andthe second switching gear element.

A for example ring-shaped, rod-shaped or otherwise similarly designedtransmission part is arranged between the carrier ring and the firstcoupling element, which transmission part can be moved about theactuating pivot axis together with the carrier ring. The transmissionpart and the carrier ring can be moved relative to one another, forexample they are rotatable and/or displaceable relative to one another.A spring arrangement is arranged between the transmission part and thecarrier ring which can be actuating by means of a relative movement ofthe transmission part and the carrier ring in order to achievespring-loading of the first setting gear element in at least one switchposition. Consequently, the carrier ring can reach a final rotationposition while the transmission part has not yet reached this finalposition and is spring-loaded in the final position by the springelement or the spring arrangement. If the first setting gear element hasa suitable position with respect to a component to be switched, forexample a gear wheel, it is pushed or adjusted into this final positionby the spring arrangement.

At least one guide cam is expediently arranged on the carrier ring or atransmission part that can be moved together with the carrier ring aboutthe actuating pivot axis, for example the above-mentioned protrudingpart which can be adjusted relative to the carrier ring in order todeflect the movement of the actuating part about the actuating pivotaxis into a linear movement of the first setting gear element. The firstcoupling element or a body associated with this or coupled to thisengaged with the guide cam. Two guide cams are preferably provided whichare arranged on opposite sides of the gearbox housing or the gearboxholding structure.

The second coupling element is expediently pivotably and/or displaceablymounted relative to the gearbox housing. Consequently it is possible forthe second coupling element, which is adjusted in a linear manner, totransfer the linear movement to the second setting gear element on thebasis of a displacement relative to the gearbox housing. However, apivot bearing or a combined pivot and thrust bearing of the secondcoupling element is also possible.

The second coupling element is expediently pivotably mounted on a pivotbearing provided on a gearbox housing, for example a bearing pin whichprotrudes from the circumference wall of the gearbox housing or abearing recess arranged in the circumference wall of the gearboxhousing. The second coupling element can also alternatively oradditionally be pivotably mounted on the actuating part. The bearingrecess can for example be achieved by a longitudinal groove. Thislongitudinal groove can also be the arch-shaped guide recess describedbelow. If bearing pins or bearing recesses are provided on the gearboxhousing, these are expediently provided on opposite sides of the gearboxhousing and/or on an area of the gearbox housing which is largest insize. Consequently, the bearing pins protrude for example in a radialdirection in front of the circumference wall of the gearbox housing.

The actuating part expediently has a guide recess which extends in anarch shape about the actuating pivot axis and engages in the onecoupling element, for example the second coupling element. Inparticular, the coupling element has a straight or curved section whichengages in the above-mentioned guide recess. It is possible for theguide recess to be of a sufficient depth for an arch-shaped moving spaceto be present in which the second coupling element can engage when itpivots about the actuating pivot axis.

The actuating part is expediently displaceably mounted in a linearmanner on a linear guide of the carrier ring. Consequently, the carrierring has a linear guide with one or more guide grooves or other linearguide elements of the like. Linear guide projections can also beprovided, for example longitudinal ribs or the like, which stick outfrom the carrier ring and engage in corresponding longitudinal guidegrooves on the actuating part. Consequently, linear guide components arepresent on the carrier ring and on the actuating part.

Advantageously there is a provision for the actuating part to be guidedon a machine housing of the manual machine tool. For example, a wall ofthe machine tool has a slot or recess in which the actuating part isarranged. Guide recesses, in particular guide grooves, pockets or thelike can be provided on one or more edge areas of the recess to guidethe actuating part.

The coupling element, in the above embodiment for example the secondcoupling element, expediently engages in a slot of the linear guide. Forexample, the linear guide has linear guide sections, between which theslot is arranged. The linear guide sections are expediently connected bymeans of connection sections. The second coupling element engagesbetween the connection sections and the actuating part.

The linear guide expediently comprises two linear guide sectionsarranged at an angular distance from one another relative to theactuating pivot axis.

Consequently, the actuating part can be guided on two or more linearguide sections, which can also be interrupted, for example by theabove-mentioned slot.

The actuating part expediently has at least one support section tosupport the gearbox housing. Consequently the actuating part issupported on one side by the carrier ring and on the other side on thegearbox housing.

It is preferable for the actuating part to have an arch-shaped orbarrel-shaped wall design. Consequently, it is advantageous for theactuating part to cover the components and/or the locking arrangement tobe actuated by it.

An embodiment can provide for the actuating part to connect longitudinalend areas of the carrier ring that are at a distance from one another toone another.

The carrier ring has a distance between its longitudinal end areas thatis bridged by the actuating part. For example, the actuating partengages in linear guide sections arranged on the longitudinal end areasuch that these linear guide sections are connected to one anotherrelative to the actuating pivot axis. The actuating part thereforecloses the carrier ring as it were.

At this point it should be noted that the carrier ring can be a closedring, in other words it fully surrounds the gearbox housing. It is alsopossible, however, for the carrier ring to only be a partial ring.Consequently, the carrier ring can be designed as a ring segment. Thecarrier ring preferably extends around at least half of the outercircumference area of the gearbox housing, in other words around atleast 180 degrees. It is preferable for the carrier ring to extendaround at least 270 to 300 degrees of the outer circumference of thegearbox housing.

The gearbox can be switched between at least two switch positions inwhich speed ratios between the gearbox drive and the gearbox output aredifferent from one another. It is advantageous in this case for thegearbox to comprise a first gear wheel arrangement and at least a secondgear wheel arrangement, each of which has at least one gear wheel and aswitching gear element. The switching gear elements and the gear wheelsof the gear wheel arrangement are preferably toothed wheels. Of course,the invention can also be used in a rolling wheel drive or frictionwheel drive.

A respective switching element is preferably mounted in a locallyadjustable manner to set the switch positions of the gearbox on the or agearbox holding structure, for example the gearbox housing, between atleast two setting positions and/or can be adjusted between an unmovableand a movable position relative to the gearbox holding structure.

The switching gear element of the first gear wheel arrangementadvantageously forms a switch actuator for the second gear wheelarrangement to switch the gearbox between two of the switch positions,which switching gear element can be switched between a first settingposition and at least a second setting position in which a movement ofthe switching gear element of the second gear wheel arrangement isdifferent relative to the gearbox holding structure and/or the switchactuator is disengaged and engaged with the at least one gear wheel ofthe second gear wheel arrangement.

The switch actuator can be directly engaged with one or more gear wheelsof the second gear wheel arrangement, for example a planetary gear setwith the second gear arrangement is tightly coupled to or engaged withthe first gear arrangement, which forms or comprises the at least onegear wheel of the first gear wheel arrangements. The planetary gear setscan no longer be rotated relative to one another and are coupled to oneanother such that they cannot rotate by means of the switching gearelement, for example a hollow wheel.

In this embodiment of the gearbox only the switching gear element of thefirst gear wheel arrangement needs to be adjusted in order to switch notonly the first gear wheel arrangement but also the second gear wheelarrangement. This makes actuation significantly easier. For example, itis easier to construct an actuation device that only needs to beconnected to or to control the switching gear element of the first gearwheel arrangement in order to act not only on the first gear wheelarrangement but also on the second gear wheel arrangement.

A configuration can provide for the switching gear element of the secondgear wheel arrangement being tightly fixed in the first setting positionof the switch actuator relative to the gearbox holding structure, inother words for example the gearbox housing, and to be rotatable in thesecond setting position relative to the gearbox holding structure. Inthe fixed position of the switching gear element of the second gearwheel arrangement, planetary gears, in other words the at least one gearwheel of the second gear wheel arrangement, can roll the switching gearelement. In the rotatable position of the switching gear element of thesecond gear wheel arrangement, the at least one gear wheel, for examplea planetary gear, can take the second gear wheel arrangement of theswitching gear element with it, or rotate it simultaneously.

The switching gear element of the second gear wheel arrangementadvantageously has at least one anti-rotation contour to engage in apositive-locking counter-contour of the gearbox holding structure and/orof the switching gear element that forms the switch actuator for thefixed regulation of the gearbox holding structure, for example thegearbox housing. The anti-rotation contour and the positive-lockingcounter-contour can for example be a pairing of teeth and spaces betweenthe teeth or teeth recesses, a pairing of an anti-rotation projectionand an anti-rotation recess, a groove structure or the like.

The switching gear element which forms the or a switch actuator can havearch-shaped teeth on its inner circumference as a positive-lockingcounter-contour, by means of which teeth in the first setting positionthe anti-rotation contour engages with the gear element, in particularthe or a switching gear element, which can be switched by the switchactuator and in the second setting position is engaged with the at leastone gear wheel of the first gear wheel arrangement, for example theradial outer teeth. For example, this gear wheel meshes with theswitching gear element or switch actuator.

In the first setting position it is advantageous if the switching gearelement which forms the switch actuator is fully disengaged from the atleast one gear wheel of the first gear wheel arrangement, in particularis out of direct engagement with the at least one gear wheel of thefirst gear wheel arrangement or all gear wheels of the first gear wheelarrangement. Consequently the switching gear element only then fulfilsthe function of a switch actuator for the other switching gear element,the switching gear element in the second gear wheel arrangement.

A configuration in which the switching gear element of the first gearwheel arrangement engages with the at least one gear wheel of the firstgear wheel arrangement, for example a planetary gear set or at least twoplanetary gears of the first gear wheel arrangement if the switchactuator is in the first switch position is also possible. This is apossible configuration in the case of a coupling of planetary gear sets,with the components of the first gear wheel arrangement and the secondgear wheel arrangement making up the configuration.

In the second setting position of the switch gear element which formsthe switch actuator, the switching gear element of the at least onesecond gear wheel arrangement, in other words the switched switchinggear element, can be rotated relative to the gearbox holding structuresuch that it can be moved along by the at least one gear wheel of the atleast one second gear wheel arrangement. Consequently the switching gearelement of the second gear wheel arrangement can rotate into the secondsetting position of the switch actuator and therefore be moved along bythe one or more gear wheels of the second gear wheel arrangement.

The switching gear element which can be switched by the switch actuatoris expediently mounted in a rotatable manner relative to the gearboxholding structure. It can also, in addition or alternatively to this, bereceived onto or into the gearbox holding structure in a linear, fixedmanner. This is advantageous in particular if the switching gear elementof the second gear wheel arrangement is fixed relative to a rotationalaxis of the gearbox output or its own rotational axis.

A bearing can be arranged on the gearbox housing or the gearbox holdingstructure for the rotatable mounting of the switching gear element whichcan be switched by the switch actuator of the second gear wheelarrangement, for example a bearing groove and a bearing projection, aroller bearing, in particular a needle bearing, ball bearing or thelike. A supporting body is preferably arranged in a locally fixed mannerrelative to the gearbox holding structure, on the outer circumferenceand/or inner circumference of which the switching gear element of thesecond gear wheel arrangement is rotatably mounted. The at least onegear wheel of the second gear wheel arrangement is also provided for therotatable mounting of the switching gear element. Consequently, theswitching gear element of the second gear wheel arrangement can berotatably mounted on one or more gear wheels of the second gear wheelarrangement or using the gear wheels. This is possible for example ifthe switching gear element of the second gear wheel arrangement isdesigned as a hollow wheel which surrounds the planetary gear set in aring and is mounted on the planetary gear set.

It is further advantageous if the switching gear element of the secondgear wheel arrangement can only be switched or actuated by the switchinggear element which forms the switch actuator or the switching gearelement of the first gear wheel arrangement. An actuating device whichfor example can be actuated directly by the operator from outside of themachine housing is therefore only linked to the switching gear elementof the second gear wheel arrangement by means of the switching gearelement of the first gear wheel arrangement and/or not directly.

The switching gear element which forms the switch actuator isexpediently displaceably mounted in a linear manner relative to thegearbox holding structure, for example parallel to a rotational axis ofthe gearbox drive and/or the gearbox output or its own rotational axis,between the first setting position and the second setting position. Theswitching gear element which forms the switch actuator is expedientlyrotatable in one, two or more in particular settings positions relativeto the gearbox holding structure. It is possible for as it were theswitching gear element of the first gear wheel arrangement to berotatable in a setting position, for example in an intermediate settingposition that is between two further setting positions. The operator canthen as it were move the switch actuator from a fixed setting positioninto a rotatable setting position relative to the gearbox housing or thegearbox holding structure by for example adjusting it in a linearmanner, rotating it or the like.

It is further advantageous if one or more, in particular all, of theswitching gear elements is/are spring-loaded in a respective switchposition. In this way, for example, the switching gear element of thesecond gear wheel arrangement can be spring-loaded by means or a springarrangement in one or both of the first and second setting positions. Ifthe teeth of one of the switching gear elements do not fit with therespective gear wheel of the first or second gear wheel arrangement tobe switched or meshed, the spring loading ensures that where the teethdo match the matching teeth glide into the respective places.

The gear wheels of the first gear wheel arrangement which are or can bein rolling engagement and the at least one second gear wheel arrangementare expediently different from one another in terms of their diameterand/or they have different roller circumferences from one another interms of their diameter for the rolling engagement with the respectiveassigned switching gear element. This means that different speed ratioscan expediently be set between the gearbox drive and the gearbox output.

The first gear wheel arrangement and the second gear wheel arrangementexpediently form a first gearbox step, wherein the gearbox has at leasta second gearbox step, for example a planetary step. The first gearboxstep is upstream or downstream of the gearbox output of the secondgearbox step. In particular, the gearbox steps are therefore arrangedsequentially one behind the other.

The second gear wheel step can be a gearbox step providing a fixed speedratio, in other words merely a gearbox step that decreases or increasesspeed and cannot be switched. A switchable configuration is, however,preferred. The second gearbox step can expediently be switched betweenat least two switch positions in which a speed ratio between a drive ofthe first gearbox step and an output of the second gearbox step isdifferent. This means, for example, a four-speed gearbox can beachieved.

The gearbox is expediently a planetary gear. Other types of gear are,however, also easily possible.

The first and/or the second setting gear element expediently comprises ahollow wheel or is formed by a hollow wheel.

The embodiment of the invention described below in greater detail in thedrawing shows a screwing machine or drilling machine. Of course theinvention can also be used in other manual machine tools, for examplemilling machines, cutting machines, saws, grinding machines, polishingmachines and the like. The gears and/or the actuating device can,however, also be used in manual machine tools, for example, which have atool holder that is driven in an oscillatory manner, for example movedbackwards and forwards in a linear manner.

The manual machine tool expediently has a tool holder for a tool and/ora tool, for example a drilling tool, screwing tool or the like. Acutting tool, milling tool or the like can, however, also be provided.

The gearbox output of the gearbox is expediently directly rotationallycoupled to a tool holder on the manual machine tool. A recess for ascrew bit, drill chuck, screw chuck or a tool chuck of the like can beprovided, for example. It is also advantageous if a striking mechanismis arranged on the gearbox output, for example an axial strikingmechanism.

It is also possible for an angle gear to be present between the gearboxand a tool holder, for example an angular gearbox or a conversiongearbox, which converts the rotating output movement of the gearboxoutput into an oscillatory linear movement or a hypercycloid and/oreccentric movement of the tool holder.

An embodiment of the invention is described below on the basis of thediagrams, in which:

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a frontal view of a manual machine tool according to themanual machine tool, which is shown in

FIG. 2 in a transverse section along cutting line A-A in FIG. 1,

FIG. 3 is an exploded diagram of a gearbox of the manual machine toolaccording to the above figures,

FIG. 4 is an exploded diagram of a powertrain of the manual machine toolincluding the gearbox and with a drill chuck,

FIG. 5 is an exploded diagram of an actuating device for the gearbox,

FIG. 6 is a lower view of an actuating part of the actuating deviceaccording to FIG. 5,

FIG. 7 is a planar view of the actuating part according to FIG. 6installed into a housing of a manual machine tool,

FIG. 8 is a lateral view of the gearbox according to FIG. 3,

FIG. 9 is a sectional view of the gearbox according to FIG. 8 along acutting line B-B in FIG. 8,

FIG. 10 is a frontal view of the gearbox according to the above figuresin the direction of sight according to FIG. 1 in a first and a secondswitch position of the gearbox,

FIG. 11 is the view according to FIG. 10 but in a third and fourthswitch position of the gearbox,

FIG. 12 is the gearbox according to the figures above in a sectionalview according to the cutting line C-C in FIG. 10 in a first switchposition,

FIG. 13 is the gearbox according to FIG. 12 but in a second switchposition,

FIG. 14 is a cross-sectional view of the gearbox according to the abovefigures in a third switch position, for example according to a cuttingline F-F in FIG. 11,

FIG. 15 is a cross-sectional view of the gearbox according to FIG. 14but in a fourth switch position,

FIG. 16 is a lower frontal view of the actuating part,

FIG. 17 is a section through the actuating part along a cutting line G-Gin FIG. 16,

FIG. 18 is a sectional view of the actuating part along a cutting lineH-H in FIG. 16,

FIG. 19 is a sectional view roughly corresponding to cutting line F-F inFIG. 11 of a modified gearbox housing of the gear and the actuating partaccording to FIGS. 16 to 18,

FIG. 20 is a perspective diagonal view of the actuating part accordingto FIGS. 16 to 18 and the assigned locking part,

FIG. 21 is a further perspective diagonal view of the actuating part andthe locking part,

FIG. 22 is a perspective view of the actuating part and the locking partwhich is engaged with a locking structure of the actuating part, and

FIG. 23 is a locking arrangement with a control surface arrangementassigned to three locking indentations in a frontal view from the frontor above.

A manual machine tool 10, for example a screwing device, has a machinehousing 11 which is preferably pistol-like in shape. An operator cangrip the machine housing 11 and therefore the manual machine tool 10using a handle section 12 which protrudes from a motor section 13 of themachine housing 11. An energy storage interface 14 is provided on a footarea or a free end area of the handle section 12 which faces away fromthe motor section 13, to which energy storage interface an energystorage device 25 such as a battery pack can be attached. Consequentlythe manual machine tool 10 can be operated in a self-sufficient andwireless manner, but it does not have to do so. A manual machine toolhaving a mains connection 14B for an AC network, in particular aconnection cable with a plug and/or a socket for a connection cable, inparticular a power cable, or a manual machine tool with an energystorage interface and a mains connection is also easily possible.

The energy storage interface 14 supplies a power supply device 15 withelectrical energy. The power supply device 15 can be actuated by meansof a switch 16 which is preferably arranged on the handle section 12 tosupply power to a drive motor 17 that is received in the motor section13 of the machine housing 11, in particular to set its speed and/ortorque.

The drive motor 17 has a motor shaft 18 which extends in a longitudinaldirection of the motor section 13. The motor shaft 18 is rotatablymounted on motor bearings 19. The drive motor 17 has for example anexciter coil arrangement 20 which is penetrated by the motor shaft 18and which is rotatably received in a rotor, in particular a permanentmagnet rotor, a squirrel-cage rotor or the like.

The drive motor 17 is arranged in the machine housing 11 in a fixedposition. Its motor shaft 18 extends from a rear wall 21 in thedirection of a front face 22 of the motor section 13. An upper side wall23 of the machine housing 11 is provided on the side of the motorsection 13 which faces away from the handle section 12. A rotationdirection alternator 24 is preferably arranged between the handlesection 12 and the motor section 13, by means of which the direction ofrotation of the drive motor 17 can be set or changed.

A hook element 26 is preferably provided on a free end area or anotherpoint in the machine housing 11 to hang up the manual machine tool, forexample on a user's belt.

A motor output 27 of the drive motor 17 drives a gearbox 40 of themanual machine tool.

The gearbox 40 has a gearbox drive 41 designed as a drive wheel and/ordrive shaft or having a drive wheel and/or a drive shaft, which gearboxdrive is connected to the motor drive 27 in a fixed manner.

A gearbox drive 42 of the gearbox drives a tool shaft 28, for example,which protrudes from the front face 22 of the machine housing 11.

The tool shaft 28 has a tool holder 29 for example for a tool 30, forexample a drilling tool, a screwing tool or the like. The tool shaft 28is for example rotatably mounted by means of a bearing 31 on the machinehousing 11. The tool shaft 28 can also be mounted directly by thegearbox 40 or on the gearbox 40, for example using a bearing 43.

It is also advantageous if in a manual machine tool according to theinvention a striking mechanism for example an axial striking mechanismand/or rotational striking mechanism is arranged on the output of thegearbox. A striking mechanism of this kind can also easily be integratedinto the gearbox. A striking mechanism 200 is provided in the specificembodiment.

An impact body 201 of the striking mechanism 200 is for example formedby the tool shaft 28 or fixed to this. The impact body 201 is forexample a ring which is penetrated by the tool shaft 28 and is connectedto the tool shaft 28 in a manner that prevents it from rotating and thatis fixed in an axial direction.

The impact body 201 is force-actuated by means of a spring 202 in aforwards direction SW1, in other words towards the tool holder 29.

The striking mechanism 200 can be switched between a described strikingoperation and a non-striking operation, for example by means of anactuation of an actuating element 206 that can be gripped by theoperator. The actuating element 206 comprises, for example, a slider ora rotary element. The actuating element 206 can be adjusted as a settingbody 207 between the switch position shown in FIG. 2 and assigned to thestriking operation in which the tool shaft 28 including the bearing 31can be displaced in a linear manner relative to the rotational axis D,in other words has an end clearance and therefore teeth 203, 204 canengage with one another, and a further switch position that is not shownin the drawing which represents a non-striking operation and in whichthe teeth 203, 204 are kept apart from one another. The bearing 31 isheld on the setting body 207. The tool shaft 28 is displaceably mountedon bearing 43 relative to the rotational axis.

The teeth 203 are arranged on an abutment body 205 which is arrangedbetween the bearing 43 and the impact body 201 and is fixed in position(prevented from rotating and fixed to prevent displacement) relative tothe machine housing 11. The teeth 203 are opposite the teeth 204arranged on the impact body 201. The teeth 203, 204 are arranged on therespective front faces of the abutment body 205 and the impact body 201.The teeth 203, 204 are preferably angular teeth. The teeth 203, 204preferably extend in a ring-shaped or partially ring-shaped manner aboutthe rotational axis D of the tool shaft 28.

If there is pressure in a direction of force SW2 on the tool shaft 28,for example if the tool 30 is loaded against the machine housing 11 bymeans of a screw or a workpiece, the teeth 203, 204 glide along oneanother, wherein they adjust the impact body 201 in the direction offorce SW2 such that a spring 202 force-actuated with a direction offorce SW1 is tensioned. If the teeth 203, 204 are further rotated fromone pair of teeth into the next pair of teeth, they can immerse into oneanother suddenly when loaded by the spring 202, such that a strikeoccurs in the direction of force SW1 on the tool shaft 28 andconsequently the tool holder 29.

An embodiment that is only partially indicated in FIG. 4 provides for arecess chuck 32, for example a drill chuck, instead of the tool shaft28, which recess chuck is suitable for holding for example the tool 30.

The gearbox 40 is a four-speed gearbox. The gearbox 40 can therefore beswitched between four gears or switch positions S1, S2, S3 and S4 whichare showing in FIGS. 12, 13, 14 and 15.

The gearbox is received in a gearbox housing 44. The gearbox housing 44has a circumference wall 45 which delimits an essentially cylindricalinner space in which the gearbox components, pinions and the like of thegearbox are essentially received. On the front face the gearbox housing44 is covered by front walls 46, 47, for example covers. The front walls46, 47 have openings 48 through which the motor drive 27 can beconnected to the gearbox drive 41 and the tool shaft 28 or the recesschuck 32 to the gearbox drive 42 of the gearbox 40. The openings 48 arefor example penetration openings.

The gearbox housing 44 is received in the machine housing of the manualmachine tool 10 in a manner that prevents it from rotating, which is whyfor example teeth 49 and/or an anti-rotation projection 49A are providedon the front wall 47 which faces aware from the tool holder 29 and/or acircumference contour 50 designed in the manner of anti-rotationprotection are provided on the front wall, which faces away from thedrive motor 17.

Consequently the gearbox housing 44 which forms a base gearbox housing(the circumference wall 45) and the front walls 46, 47 which form thecovers essentially tightly enclose the gearbox components of the gearbox40 described below, which is which sealing elements, in particulartextile seals, plastic seals, O-rings, labyrinth seals etc. can beprovided.

The gearbox 40 has a first gear step G1 and a second gear step G2. Thefirst gear step G1 forms an initial gear step and can be driven by thegearbox drive 41. The second gear step G2 forms an output gear step anddrives the gearbox output 42 of the gearbox 40.

DETAILED DESCRIPTION

The gear steps G1 and G2 are planetary gear steps. Overall, the gearbox40 is designed as a planetary gearbox.

The gear step G1 comprises a sun wheel 51 which is arranged on the drivewheel or gearbox drive 41 or is in one piece with the gearbox drive 41.The sun wheel 51 meshes with the planetary gears 51 which are rotatablymounted on a bar or planetary gear support 53. For example the planetarygears 52 are rotatably mounted on axis elements 55 which protrude infront of a carrier body 54. The planetary gears 52 can be mounteddirectly onto the axis elements 55 or as preferred in the embodiment bymeans of roller bearings 56, in particular ball bearings or needlebearings, which improves the rotatability and the bearing. On the onehand the axis elements are on opposite sides of the carrier body 54 andon the other hand there is an output 57 on the carrier body which formsa sun wheel 58 for the second gear step G2. Teeth 59 are provided on aradial outer circumference of the planetary gear support 53 or thecarrier body 54.

The planetary gears 52 form a planetary gear set 60, to which a firsthollow wheel 61 and a second hollow wheel 62 are assigned.

The planetary gears 52 are step planetary gears as it were. Theplanetary gears 52 have roller circumferences 63, 64 with differentdiameters which are assigned to the first and the second hollow wheelsor mesh with these when a corresponding switch position of the gearbox40 is set.

The hollow wheel 61 is mounted in a rotatable manner in the gearboxhousing 44 but cannot be displaced in an axial direction.

In the embodiment the hollow wheel 61 is received between the front wall46 and the steps 65 of the planetary gears 52 in a sandwich-like manner.

The hollow wheel 61 is for example supported on its opposite front facesdirectly or indirectly on the front wall, and opposite this on the otherfront face on a step 65 provided between the roller circumferences 63,64. A bearing plate 66 is preferably provided between the hollow wheel61 and the front wall 46, which bearing plate is received inside thecircumference wall 65 in rotatable manner or preferably in a fixedmanner to prevent rotation as shown in FIG. 4 by means of correspondingouter circumference contours or rotation positive-locking contours.

It is also possible for the hollow wheel 61 to be held in anon-displaceable manner relative to a rotational axis D of the gearboxoutput 42 of the gearbox, for example by means of ring contours whichare engaged with a support body 61 described in greater detail below. Aring projection can for example protrude in a radial, outwards directionin front of the support body 61 and engages in a ring groove on theinner circumference of the hollow wheel.

In the sense of a stabilisation or a mechanically resilient structure,it is also possible for the axis element 55 to be supported on a supportbody 67 on the free ends which face away from the carrier body 54. Thesupport body 67 has recesses 68 for at least one of the axis elements55. Support projections 69 are also provided which as it were delimitrecess chambers or recess spaces for the planetary gears 62. It ispossible but not essential for part of the axis element 55, inparticular an axis element 55 which does not support any planetary gearsto engage in the support projections 69 in a positive-locking manner,which is why the support projections 69 have recesses 69A for example.The planetary gears 52 are as it were received between the planetarygear support 53 and the support body 57 in a sandwich-like manner androtatably mounted on the planetary gear support 53, namely the axiselements 55 of this.

It is understood that the support body 67 and the carrier body 54 canalso be in one piece. The support body 67 is also optional, in otherwords the carrier body 54 would be sufficient to rotatably mount theplanetary gears such that the support body 67 is not present in thiscase.

While the first hollow wheel 61 is mounted in the gearbox housing 44 ina rotatable but non-displaceable manner, the second hollow wheel 61 ismounted in the gearbox housing in a displaceable but non-rotatablemanner relative to a setting axis SA. Anti-rotation projections 70 areprovided on the radial outer circumference of the second hollow wheel 62and engage in the anti-rotation recesses 71 of the gearbox housing 44.The anti-rotation projections 70 are preferably designed in the mannerof slot grooves, cam followers or the like. They engage in theanti-rotation recesses 71. The anti-rotation recesses 71 are for exampledesigned as longitudinal grooves 72 which run in parallel to the settingaxis SA. The anti-rotation recesses 71 or longitudinal grooves 72 extendfor example on the inside or on the inner circumference of thecircumference wall. The anti-rotation projections 70 and/or theanti-rotation recesses may have different cross-sectional contours, forexample have a wider or narrower design in the peripheral direction. Itis not specifically about ensuring fundamental functionality that thehollow wheel 62 can be adjusted along the setting axis SA or in parallelto the setting axis SA on the gearbox housing 40 and/or relative to theplanetary gear set 60.

In the switch position shown in FIG. 12 and FIG. 14, namely the firstswitch position S1 and the third switch position S3, the second hollowwheel 52 is in a setting position P1 relative to the setting axis SA inwhich the second hollow wheel holds the first hollow wheel 61 in thegearbox housing in a manner which prevents it from rotating such thatthe planetary gears 52 mesh with inner teeth 75 of the first hollowwheel 61 with their smaller roller circumferences 63 and roll on theinner teeth 75. The second hollow wheel 62, which is received in thegearbox housing in a manner which prevents it from rotating, hasanti-rotation contour on its inner circumference to hold the firsthollow wheel 61 which has corresponding complementary rotationalpositive-locking contours on its outer circumference in a manner whichprevents it from rotating. These rotational positive-locking contoursand complementary rotational positive-locking contours are provided byinner teeth 73 of the second hollow wheel 62 and outer teeth 74 of thefirst hollow wheel 61, which can engage with one another in apositive-locking manner. Consequently the inner teeth 73 of the secondhollow wheel 62 have on the one hand the function that the planetarygears 52 can roll on them and on the other hand the function of holdingthe first hollow wheel 61 in a manner which prevents rotation relativeto the gearbox housing 44 and consequently also the machine housing 11of the manual machine tool 10.

If the second hollow wheel takes the setting position P2 shown in FIGS.13 and 15 relative to the setting axis SA, the first hollow wheel 61 isreleased for rotation. Consequently, the planetary gears 52 and theplanetary gear set 60 can take the first hollow wheel 61 along with therotation and experience no or minimal resistance as a result of thehollow wheel. In this situation, the planetary gears 52 roll with theirlarger roller circumferences 64 on the inner circumference, andconsequently the inner teeth 73 of the second hollow wheel, which isessential for the switch positions shown in FIGS. 13 and 15, the secondswitch position S2 and the fourth switch position S4, of the gearbox 40.The output 57 of the first gearbox step G1 rotates into the second andfourth switch position at a high speed and with a lower torque than inthe first and third switch position S1, S3.

The gear step G2 comprises planetary gears 76 of a planetary gear set 77which engage on the one hand with the sun wheel 58, in other words theoutput of the first gear step G1, and on the other hand with a thirdhollow wheel 78. The third hollow wheel 78 is received in the gearboxhousing 44 in a manner that is displaceable along a setting axis SB. Thesetting axis SA can be coaxial or parallel to the setting axis SB. Thesetting axes SA, SB are shown in FIGS. 12 and 13 by way of an example.

The setting axes SA, SB can also, for example, be coaxial with or concurwith a rotational axis D of the gearbox 40 and/or the gearbox drive 41and/or the gearbox output 42. The rotational axis D of the gearbox 40 issimultaneously the rotational axis of the drive motor 17 such thatultimately the gearbox 40, the drive motor 17 and the gearbox output 42are coaxial. The tool holder 23 also rotates about the rotational axisD.

The planetary gears 76 are rotatably mounted on a planetary gear support79, in other words a bar. The planetary gear support 79 has a carrierbody 80 with the axis element 81 arranged on one side and the gearboxoutput 42 arranged on the opposite side. The axis elements 81 protrudefrom the sun wheel 58 and consequently the output 57 of the first gearstep G1 such that the planetary gears 76 rotatably mounted on the axiselements 81 or rotatably mounted by the axis elements 81 are engagedwith the output 57 or can be driven by this. The planetary gears 76 canbe directly or indirectly rotatably mounted on the axis elements 81, forexample by means of roller bearings, in particular needle bearings.

The planetary gear set 77 comprises for example four planetary gears 76while the planetary gear set 60 comprises three planetary gears 52.These figures should not, however, be understood as restrictive. Oneplanetary gear set can very much also comprise two planetary gears, fiveplanetary gears or another number of planetary gears.

The radial outer circumference of the hollow wheel 78 has anti-rotationprojections 83 which are engaged with the anti-rotation recesses 84 onthe gearbox housing 44, for example these can be applied to the cover orthe front wall 47. In the switch positions S1 and S2 of the gearbox 40shown in FIGS. 12 and 13, the third hollow wheel 78 takes on a settingposition P3 relative to the setting axis SB in which the third hollowwheel 78 is fixed in a manner which prevents rotation relative to therotational axis D or the gearbox housing 44. The anti-rotationprojections 83 then engage in the anti-rotation recesses 84.

In a setting position P4 relative to the setting axis SB, however, theanti-rotation projections 83 of the third hollow wheel 78 are arrangedfree from or beyond the anti-rotation recesses 84 such that the hollowwheel 78 can rotate about the rotational axis D.

In setting position P3, the fixed position of the third hollow wheel 78to prevent against rotation, the outer circumferences of the planetarygears 78 roll on inner teeth 85 of the hollow wheel 78. The second gearstep G2 causes a reduction and speed and therefore an increase in torquefrom its input side to its output side or from its drive to its gearboxoutput 42.

In the setting position P4 of the hollowing wheel 78, however, thewheels 76 continue to be engaged with the inner teeth 85. The innerteeth 85 of the hollow wheel 78, however, continue to be engaged withthe outer and radially outer teeth 59 or the planetary gear support 53.The hollow wheel 78 is therefore fixed in a manner which preventsrotation relative to the planetary gear support 73. In addition to this,the planetary gears 76 are mounted in a manner which prevents rotationbetween the teeth of the sun wheel 78 and the inner teeth 85 of thethird hollow wheel 78. Consequently, in this situation the secondgearbox step D2 has a speed ration of i=1 between an input side and anoutput side and therefore does not cause either a change in speed or achange in torque.

The gearbox output 42 is provided on the planetary gear support 79. Theplanetary gear support 79 has support projections 86 which protrude fromthe carrier body 80, between which for example the tool shaft 28 can bearranged or by which the tool shaft 28 can be held. For example the toolshaft 28 is held by support elements 87 which in turn are supported onthe support projections 86.

The gearbox drive 41, which can also be called a drive shaft, isrotatably mounted on a pivot bearing 88, in particular on a rollerbearing, in the embodiments shown in FIGS. 12 to 14. The pivot bearing88 is supported on an inner circumference of an opening of the supportbody 67 and is for example axially secured relative to the rotationalaxis D by means of a snap ring 89.

In the bearing concept shown in FIG. 15, however, the support body 67 isrotatably mounted on the cover or the front wall 46 of the gearboxhousing 44 by means of a pivot bearing 90. The pivot bearing 90, forexample a ball bearing, needle bearing or other roller bearing (a slidebearing is also possible) is for example arranged and supported in theopening 48.

An actuating device 100 is used to switch and actuate the gearbox 40.The hollow wheel 78 can be adjusted in a linear manner between thesetting positions P3, P4 using the actuating device 100. The hollowwheel 78 forms a first switching gear element 101. The hollow wheel 62can also be adjusted in a linear manner between the setting positions P1and P2 using the actuating device 100 and is coupled to the actuatingdevice 100 in order to do this. The hollow wheel 62 forms a secondswitching gear element 102.

A third switching gear element 103 is not switched directly by theactuating device 100 but instead by the switching gear element 102 inbetween. The switching gear element 103 is provided by the hollow wheel78.

The planetary gear set 60 forms a components of a first and a secondgear wheel arrangement 104, 105, see FIG. 14. The first gear wheelarrangement 104 is assigned to the first switching gear element 102 andcomprises for example the roller circumferences 64 of the planetarygears 52. The second gear wheel arrangement 105 is as it were coupled orconnected tightly to the first gear wheel arrangement at least in termsof the planetary gears 52. Each planetary gear 52 has various rollercircumferences 63, 64 and therefore forms two partial planetary gears.The partial planetary gear with the roller circumference 63 is assignedto the hollow wheel 61 and therefore to the switching gear element 103and the gear wheel arrangement 105 as a gear wheel 105A. The partialplanetary gear with the roller circumference 64 is assigned to thehollow wheel 62 and therefore to the switching gear element 102 and thegear wheel arrangement 104 as a gear wheel 104A. The partial planetarygears are in one piece or coupled tightly to one another as a result oftheir design as stepped planetary gears. It is easy to imagine, however,that the partial planetary gears can also be individual planetary gearsthat are connected to one another in a manner which prevents rotation orare rotatable relative to one another in a different embodiment.

The switching gear element 102 acts on the one hand as an activeswitching element relative to the gear wheel arrangement 104 by beingdirectly engaged with the larger roller circumferences 64 of theplanetary gears 52 in the setting position P2. In the setting positionP1, however, the hollow wheel 62 is adjusted away from the planetarygears 52, in other words the inner teeth 73 no longer mesh with theroller circumferences 64.

In the setting position P1, however, the hollow wheel 62 is a switchactuator for the other hollow wheel 61 which is held in a manner whichprevents rotation by the hollow wheel 62 or the switching gear element102 relative to the gearbox housing 44 which forms a gearbox holdingstructure 44A by means of the interlocking teeth, namely the outer teeth74 and therefore an anti-rotation contour 93 and the inner teeth 73 andtherefore a positive-locking counter-contour 94. Consequently, theswitching gear element 103 is as it were switched by the switching gearelement 102.

At this point it should be noted that teeth are not absolutely essentialbetween the switching gear elements 102, 103 or the hollow wheels 61,62. For example the switching gear element 102 can only adjust theswitching gear element 103 in the direction of a positive-lockingcounter-contour that is fixed in the housing or locally fixed, inparticular on the front wall, such that an anti-rotation contour 92 ofthe switching gear element 103 with the positive-locking counter-contour91 can be adjusted into a hold that prevents the switching gear element103 from rotating relative to the gearbox holding structure, in otherwords the gearbox housing 44 (FIG. 13). The anti-rotation contour 92 isfor example a positive-locking projection that runs in parallel to thesetting axis SA; the positive-locking counter-contour 91 is acorresponding positive-locking recess, for example a blind hole. Teethas anti-rotation contours and positive-locking counter-contours are,however, advantageous.

No direct coupling between the actuating device 100 and in particularthe actuating part 110 of this and the switching gear element 103therefore needs to be provided to switch the gear wheel arrangement. Thestructure of the actuating device is therefore simpler. The gearbox 40is built shorter. The actuating device 100 is also simpler and morecomfortable to handle, as will become clearer below.

The actuating device 100 comprises the actuating part 110 with anactuating handle 111. The actuating handle 111 is an opening 33 arrangedon an upper side wall 34 of the housing 11 of the manual machine tool 10and therefore easily accessible for a user.

Numbers 1, 2, 3 and 4 or other markings 35 can be arranged on thehousing 11, for example on the edge areas of the opening 33, whichmarkings are assigned to the respective switch positions S1, S2, S3 andS4. The actuating handle 111 can be displaced and/or pivoted within theopening 33. The actuating handle 111 can be adjusted into the region ofa respective marking 35, in this case therefore into a corner region ofthe opening 33 to set the switch positions S1, S2, S3 and S4. Directswitching or setting of the actuating handle 111 from each of the switchpositions S1, S2, S3 and S4 into each of the other switch positions S1,S2, S3 and S4 without setting an intermediate switch position ispossible. The gearbox 40 can for example be adjusted directly from theswitch position S1 (actuating handle 111 is shown as a dashed line inFIG. 7) into the switch position S4 (actuating handle 111 is shown as asolid line in FIG. 7) without stopping at the intermediate switchpositions S2 or S3.

The actuating handle 110 is provided on an upper side 114 of an inparticular barrel-shaped or curved wall body 112, the lower side 113 ofwhich faces towards the gearbox housing 44. A curvature of the wall body112 corresponds approximately to a curvature of the circumference wall45 of the gearbox housing 44 such that the wall body 112 can be movedalong the circumference wall 45 in the manner of a cover or a cover partor wall section.

The actuating part 110 is arranged on a traction tine 120, which in turnis pivotably mounted on the gearbox housing 44 in a pivotable orrotatable manner, in particular on the outer circumference of thecircumference wall 45 about a pivot axis MA which preferably concurswith the rotational axis D of the gearbox output 42. This means theactuating part 110 can pivot about the pivot axis MA and therefore anactuating pivot axis BS between actuating positions D1 and D2.

The carrier ring 120 has a ring body 121 which is rotatably mounted in aring guide 145 of the gearbox housing 44. The narrow sides of the ringbody 121 are for example guided by circumference projections 146 whichprotrude from the circumference wall 45.

A linear guide 123 for the actuating part 110 is provided in the freelongitudinal end areas 122 of the carrier ring 120 such that this isrotatably mounted on the carrier ring 120 along an actuatinglongitudinal axis BL between actuating positions L1 and L2.

The linear guide 123 comprises linear guide sections 124 arrangeddirectly on the longitudinal end areas 122, which longitudinal guidesections are arranged at an angular distance from one anothercorresponding to the angular distance between the longitudinal end areas122. Consequently the actuating part 110 is as it were a connecting linkor a binding link which connects the longitudinal end areas 122 of thecarrier ring 120 to one another.

Linear guide projections 115 are provided on the lower side 113 of theactuating part 110, which linear guide projections engage in the linearguide sections.

The longitudinal end areas 122 of the carrier ring 120 already have awidth or a length corresponding to the actuating longitudinal axis BLsuch that they are in principle sufficient for the linear guidance ofthe actuating part 110. Furthermore, the actuating part 110 can beguided into guide recesses, for example grooves, on the outercircumference, for example longitudinal sides and/or transverse sides,or the slot or opening 33 of the upper side wall 34.

There is additional and improved support, however, in the form ofsupport projections 129 which protrude in front of the longitudinal endareas 122 of the carrier ring 120 relative to the actuating longitudinalaxis BL or the rotational axis. Further linear guide sections 125 areprovided on the support projections 122 in which the linear guideprojections 115 engage and by means of which the linear guideprojections 115 are guided relative to the actuating longitudinal axisBL. The linear guide sections 124, 125 are for example longitudinalgrooves, the transverse width of which roughly corresponds to atransverse width of the linear guide projections 115 relative to theactuating longitudinal axis BL.

An embodiment could provide for guide cams to be provided on thelongitudinal end areas 122 of the carrier ring 120 in the manner of theguide cams 133 described below in greater detail, with which a firstcoupling element 140 which in turn is connected to the switching gearelement 101 and therefore the hollow wheel 78 can be driven.

The guide cams 133 are, however, provided on a transmission part 130,which in turn can be rotated relative to the actuating pivot axis BS ora rotational axis of the carrier ring 120. The transmission part 130 hasa ring body 131, on the longitudinal end areas 132 of which the guidecams 133 are provided. The longitudinal end areas 132 are for exampledesigned in the manner of plate bodies. A ring slot 137 is providedbetween the longitudinal end areas on the ring body 131, in other wordsan intermediate space between ring sections 138 which extend between thelongitudinal end areas 132.

The transmission part 130 is arranged in an inner space of the carrierring 120. A carrier 136 protrudes from a radial outer circumference ofthe ring body 132, which carrier is coupled to a carrier 126 of thecarrier ring 120 in a manner which permits movement. Fixed couplingwould also be possible here. The carrier 126 is, however, displaceablyor rotatably mounted on the carrier ring 120. The carrier 127 is movablymounted in a cam 127 of the carrier ring 120. The cam 127 extends on thecarrier ring in a ring-like manner. It is provided on the ring body 121.The carrier protrudes in a radial direction inwards in front of the ringbody such that it can engage with the carrier 136. A plug connectionbetween the carriers 126, 127 [sic—136] is provided, for example. Thecam 127 is therefore arch-shaped or ring-shaped and extends about thepivot axis MA of the carrier ring 120 in order to pivot the carrier ring120 relative to the gearbox housing 44.

The carrier is spring-loaded by means of a spring arrangement 128, forexample a coil spring. If the carrier ring 120 is pivoted about thepivot axis MA, the carrier 126 is also moved such that supported by thespring arrangement 128 this rotational movement or rotational force isapplied to the transmission part 130 which ultimately converts therotational movement into a linear movement for the coupling element 140and the switching gear element 101.

The coupling element 140 is for example formed by a spring bow 141.Longitudinal ends 142 of the coupling element 140 protrude in front of aring section of the coupling element 140 in a radial direction andengage in the guide cams 133 in the manner of cam followers. The guidecams 133 are for example angular cams. A coupling part recess 143, forexample a ring groove, is provided on the switching gear element 101 inthe radial direction, in which coupling part recess the coupling element140 engages, in particular with the ring section 144. A certain springproperty also brings the elastic longitudinal ends 142 of the couplingelement 140 with it such that ultimately the spring arrangement 128would not be necessary.

An indentation 147 can be provided on the ring guide 145 in which thering body 131 and consequently the transmission part 130 engage for thelongitudinal end areas 132 of the transmission part 130, resulting in acertain locking effect.

The longitudinal ends 142 of the coupling element 140 which is arrangedinside the gearbox housing 144 protrude through slots or longitudinalgrooves in front of the circumference wall 45 and engage in the guidecams 133. If, therefore, the actuating part pivots about the actuatingpivot axis BS, the carrier ring 120 also pivots about the pivot axis MAat the same time, wherein this pivot movement is deflected by adeflection gear 135 which among other things comprises the guide cams133 and the coupling element 140 and in particular its longitudinal ends142 into a linear setting movement for the setting element 101 betweensetting positions P3 and P4.

Unlike in the embodiment, in principle the transfer of the linearmovement of the transmission part 110 relative to the actuatinglongitudinal axis BL could be transferred directly into a linearactuating movement of a second coupling element 150 which is arrangedbetween the actuating part 110 and the switching gear element 102. Inthis case, however, the coupling element 150 is pivotably mounted abouta pivot axis S such that a linear adjustment of the actuating part 110along the actuating longitudinal axis BL in a direction in a linearadjustment of the setting gear element 102 is deflected into an oppositedirection.

The coupling element 150 comprises a spring bow 159. The couplingelement 150 comprises an actuating section 151 which engages in a guiderecess 116 on the lower side 113 of the actuating part 110. Furthermorethe actuating section 151 is received in a slot 124A between the linearguide sections 124, 125 of the carrier ring 120.

The spring bow 159 or the coupling element 140 is pivotably mounted onthe gearbox housing 44 about the pivot axis S. The pivot axis S isbetween the actuating section 151 and the carrier projections 154 on thefree end areas of the coupling element 150. Bearing recesses 157 areformed on the coupling element 150 between the carrier projections 153in which the bearing pins 156 which protrude in a radial outer directionin front of the gearbox housing 44 or the circumference wall 45 engage.The bearing recesses 157 can be found between the actuating sections 152and the carrier sections 153 of the coupling element 150. The actuatingsections 152, 153 are as it were levers which stick out from the pivotaxis S.

The carrier projections 154 which are for example thin wire ends engagein carrier indentations 155 of the switching gear element 102, andconsequently therefore the hollow wheel 62. For example, holes or as inthe embodiment grooves are provided as carrier indentations 155.

The second coupling element 150 extends in an arch shape about theswitching gear element 102 but is only in contact with the switchinggear element 102 in the region of the carrier recesses 154. In contrastto this, the coupling element 140 is ring-shaped as a result of its ringsection 144 and engaged with the switching gear element 101 over alarger length.

In contrast to the coupling element 140, the coupling element 150 isarranged outside of the gearbox housing 44. Its carrier projections 154stretch in an inner radial direction relative to the actuating pivotaxis BS or the pivot axis MA in front of the carrier sections 153 andpenetrate slots 158 on the gearbox housing 44 or circumference wall 45such that they are engaged with the carrier indentations 155 of thehollow wheel 62 or the switching gear element 102.

The actuating device 100 can also be locked by means of a lockingarrangement 160. The locking arrangement 160 comprises a locking part161 which can engage in locking indentations 164 on the actuating part110, for example on the lower side 113 of the wall body 112. The lockingpart 161 is spring-loaded by a spring 162 into its locking positivewhich engages in the locking indentations 164. The spring 162 andpreferably the locking part 161 are received and/or guided in a recessor on a recess 163 of the gearbox housing, for example a cylindricalrecess. Each locking indentation 164 is assigned to one of the switchpositions S1, S2, S3 and S4 of the gearbox 40.

The operator can move the actuating part 110 into the actuatingpositions assigned to the respective switch positions relative to theactuating longitudinal axis BL and the actuating pivot axis BS, in whichlocking is expediently possible. The actuating part 110 can for examplebe locked and/or positioned in the actuating positions L1, D1 to set theswitch position 1; in actuating positions L2, D2 to set switch positionS2; in actuating positions L1, D2 to set the switch position S3 andfinally in actuating positions D2, L2 to set the switch position S4.

The carrier ring 120 follows the movement of the actuating part 110about the actuating pivot axis BS. The spring arrangement 128 therebyuncouples the actuating movement from the actual setting movement.

A spring system is also provided in connection with the coupling element150. For example, the carrier sections 153 can spring or bend in anelastic manner relative to the actuating sections 151 and/or 152. Thisis achieved on the one hand by the design of the coupling element 150 asa spring bow 159. It is also, however, facilitated or improved by thefact that the bearing recess 157 is formed by a turning of the springbow 159 such that the carrier sections 153 are elastic relative to thecarrier actuating sections 152 relative to the pivot axis S.

FIG. 15 indicates that the switching gear element 102 can in principlealso be used to couple the gear wheel arrangements 104 and 105 to oneanother in a manner which prevents them from rotating. For example, theswitching gear element 102 in a setting position P2B is simultaneouslyengaged in both gear wheel arrangements 104 and 105 in a manner whichprevents rotation and can rotate within the gearbox holding structure44A or the gearbox housing 44. The switching gear element 102 whichforms the switch actuator is therefore simultaneously engaged with bothgear wheel arrangements 104 and 105. A ring groove or another slot ofthe like can for example be provided in the gearbox housing to ensurerotational freedom of the switching gear element 102.

The spring bow 159 or the coupling element 150 is pivotably mounted onthe gearbox housing 44 about the pivot axis S such that a respectiveslide actuation of the actuating part 110 in a first direction isdeflected into an opposite linear movement of the switching gear element102. It is possible, however for the coupling element 150 for example tobe coupled to the actuating part 110 in a fixed manner such that theabove-mentioned reversal of movement does not occur or in other wordsthe movement directions of the actuating part 110, the coupling element150 and the switching gear element 102 run in parallel.

It is possible for the same gear gradations to be possible in the samesetting positions of the actuating part 110 as in the case of theconfiguration described above, if the gearbox 40 is for example modifiedas follows and as indicated schematically in FIG. 14. In thisconfiguration, for example, the planetary gears 52 are arranged on theplanetary gear supports 53 such that the smaller roller circumference 63is closer to the carrier body 54 than the larger roller circumference64. This is indicated with a planetary gear 52B which is as it wererotated about 180° as the planetary gear 52 is arranged on the planetarygear support 53. If the radial inner hollow wheel which meshes with thesmaller roller circumference is arranged closer to the carrier body 54(which is indicated with a hollow wheel 61B in FIG. 14), the geartranslations which can be set by means of the linear adjustment of thehollow wheel 62 between the setting positions P1 and P2 are preciselythe reverse of those in the embodiment described above.

The locking arrangement 160 ensures that the actuating part 110 can beactuated in actuating positions B1, B2, B3 and B4 shown in FIG. 7correspond to the switch positions S1, S2, S3 and S4 in the manner of atilt-resistant or multi-stable toggle. The locking part 161 is deflectedby a control surface arrangement 165 starting from intermediate settingsor intermediate positions lying between the actuating positions B1-B4into the respective actuating position B1, B2, B3 or B4.

The control surface arrangement 165 comprises for example narrowvertices 166, 167 which cross one another. The vertex 166 divided thevertex 167 as it were into vertex sections 167A, 167B. The locking part161 cannot steady itself on the vertices 166, 167, but rather is in anunstable position or has an unstable position such that it is guidedpast the vertex 166 or 167 along gliding surfaces 168 or 169 in thedirection of the direction of one of the locking indentations 164. Apair of gliding surfaces 168, 169 faces one another in each case andforms a depression or channel. When a locking part 161 glides along oneof the gliding surfaces 168 or 169, it is as it were deflected into thedepression or channel 170, which in turn leads to the lockingindentation 164.

The depressions 170 run in a star shape to the point of intersection ofthe vertices 166, 167. These are elongated and straight in shape but canalso easily be curved at least in sections. The locking indentations 164are in the respective corner areas of a rectangle or a square. Thecontrol surface arrangement 164 extends between the locking indentations164.

The locking indentations 164 have for example an approximately sphericalinner contour or the shape of a spherical calotte. The spherical innercontour or calotte contour does not need to be closed or homogeneous butrather can be formed by support surfaces or surface sections in theregion of an envelope surrounding a ball.

The gliding surfaces 168, 169 extend as sloping surfaces from thevertices 166, 167 into the locking indentations 164.

The locking part 161 has a spherical or at least convex curved glidingsurface to glide along the control surface arrangement 165 or thelocking structure 180. The curvature of the gliding surface 161A isdesigned such that the locking part 161 is prevented from taking up astable position on the vertices 166, 167 and instead is unstable thereso the locking part 161 is guided into one of the locking indentations164. The gliding surface 161A can optionally be coated withpolytetrafluorethylene or another coating of the like.

The advantage of the spring arrangement 168 in connection with thelocking arrangement 160 is acknowledged. When the locking part 161 isdeflected into one of the locking indentations 164, the springarrangement 128 is tensioned at the same time so that ultimately thegearbox 40 can be switched into one of the switch positions S1-S4. Theforce which acts from the actuating device 100 and consequentlytherefore the actuating part 110 on the spring arrangement is amongother things affected by the inclination of the gliding surfaces 168,169.

A depth T of a locking indentation 164 is equal relative to the vertices166, 167 regardless of an actuation about the actuating pivot axis BS oralong the actuating longitudinal axis BL but not a pivot point pathwaySD relative to a pivoting of the actuating part 110 about the actuatingpivot axis BS or linear setting length SL of the actuating part 110 inthe event of a linear adjustment along the actuating longitudinal axisBL.

The setting length SL corresponds to the distance between the lowestpoint in the locking indentation 164 and the vertex 170 which runstransverse to the actuating longitudinal axis BL.

The pivot point pathway SD corresponds to the distance between thevertex 166 which runs in parallel to the actuating pivot axis BS and thelowest point of a respective locking indentation 264.

The pivot point pathways SD is shorter than the setting length SLresulting in an incline WD relative to a rotational movement about theactuating pivot axis BS as an incline WL which shifts the glidingsurfaces 169 in response to an actuation of the locking structure 180 orthe actuating part 110 on which the locking structure is arranged in thedirection of the actuating longitudinal axis BL.

In practice, it has been shown that for example a slope or an incline ofa gliding surface for a linear adjustment movement, for example theincline WL should be at least 20 degrees, preferably at least 25degrees, more preferably 30 degrees. A rotational actuation of thelocking structure 180 relative to the locking part 161 can be associatedwith a lower incline in the assigned gliding surface. For example in theincline WD a slope of at least 10 degrees, preferably at least 15degrees or 20 degrees is advantageous. Of course larger inclinations ofslopes can also be provided in the inclines WD or WL.

The design or the spring deflection of the locking part 161 has forexample a further influence on optimal locking or control in thedirection of the respective actuating positions B1-B4. If the lockingpart has a longer spring deflection, in other words the respectivesetting length of the locking part is greater, steep gliding surfaces orgliding surfaces with a steeper incline can for example be achieved. Thesetting pathways of the locking part must be sufficient to adjust thelocking part into the respective locking indentation, so for examplemust have the depth T as a minimum. In order to enlarge the settingpathways of the locking part 161, this can be supported in the machinehouse 111 at a greater distance from the locking structure 180. Ameasure of this kind is indicated in FIG. 19. In the arrangementaccording to FIG. 5, the locking part 161 is supported on thecircumferential wall 45 of the gearbox housing 44. A modified gearboxhousing 44B of a gearbox 40B, which otherwise corresponds to the gearbox40, can for example have a cover 46B on which a recess 1636 for thelocking part 161 or the spring 162 is provided. The inner circumferenceof the gearbox housing 44B is then fully retained to receive for examplethe hollow wheels 61, 62 although the recess 1636 is more likely to becloser to the rotational axis of the hollow wheels 61, 62 than therecess 163.

In a locking arrangement 260 according to FIG. 23, a bolt-like lockingpart in the manner of the locking part 161, a ball or the like isprovided as a locking part 261 to engage in locking indentations 264 ofa locking structure 280. The locking indentations 264 are for exampleassigned to actuating positions B1, B2 and B3, which is advantageous ina three-speed gearbox. The locking indentations 264 are arranged atcorner points of a triangle. Gliding surfaces 268, 269 run from arespective locking indentation 264 to vertices 266A, 266B, 266C. Thevertices 266A, 266B, 266C run in a star shape to a vertex point 267. Ifthe locking part 261 lies on the vertex point 267 or one of the vertices266A, 266B, 266C, it takes on an unstable position such that it isdeflected along the gliding surfaces 268, 269 in the direction of one ofthe locking indentations 264. A pair of gliding surfaces 268 or 269 hasgliding surfaces 268, 269 which face one another, between which adepression 270 is formed. Each depression or channel 270 runs to one ofthe locking indentations 264.

It is possible for example for the locking part 261, in particular asprung sphere, to be arranged on the actuating part 110 while thelocking structure 180 including the control surface arrangement 165 canbe arranged on the outer circumference of the gearbox housing 44. Ofcourse the reverse configuration is also possible, in other words thatthe locking part 261 is supported on the machine housing 11, for examplethe gearbox housing 44 or the cover 46B of this while the lockingstructure 280 is arranged on an actuating part 210 (shown with a dashedline in FIG. 23). The actuating part 210 is for example mounted on themachine housing 11 in a manner which permits sliding and/or a mannerwhich permits pivoting in order to adjust the three-speed gearbox thatis not shown in the drawing between its setting positions or threegears.

The invention claimed is:
 1. A manual machine tool having a drive motor,a gearbox and a tool holder, wherein a motor drive of the drive motorwith a gearbox drive of the gearbox and a gearbox output of the gearboxwhich can be rotated about a rotational axis is coupled to the toolholder in a manner which permits rotation, wherein the manual machinetool has an actuating device to adjust the gearbox between its switchpositions in which the speed ratios between the gearbox drive and thegearbox output are different, wherein the actuating device has anactuating part which is movably mounted relative to a machine housing ofthe manual machine tool between actuating positions assigned to theswitch positions of the gearbox and which can be manually actuated by anoperator of the manual machine tool, which is coupled to the at leastone switching gear element by means of a coupling element to set theswitch positions, and wherein the actuating device used to lock theactuating part in the actuating positions has a locking arrangement withlocking indentations arranged on a locking structure which are assignedto actuating positions of the actuating part and with a locking part toengage in the locking indentations, and wherein the locking structurehas a control surface arrangement with gliding surfaces along which thelocking part can glide and which extend starting from at last twolocking indentations to a vertex which is arranged between the lockingindentations and protrudes in front of the locking indentations, whereinthe locking part has an unstable position on the vertex such that thelocking part is guided past the vertex into one of the lockingindentations adjacent to the vertex.
 2. The manual machine toolaccording to claim 1, wherein the vertex is straight or curved in fullor in sections.
 3. The manual machine tool according to claim 1, whereinthe locking structure has at least three or four locking indentations,between which a vertex is arranged in each case, on which vertex thelocking part has an unstable position and from which vertex a glidingsurface extends out to the respective locking indentation in each case.4. The manualManual machine tool according to claim 3, wherein thevertices run in a star shape and/or cross one another.
 5. The manualmachine tool according to either claim 3, wherein the lockingindentations are at equal angular distances from one another and/or arearranged in corner areas of an in equal-sided polygon.
 6. The manualmachine tool according to claim 1, wherein at least one of the lockingindentations is assigned to gliding surfaces which face one another,between which a channel or a depression is formed which extends from thelocking indentation to the vertex.
 7. The manualManual machine toolaccording to claim 1, wherein exactly one single vertex is presentbetween two adjacent locking indentations.
 8. The manual machine toolaccording to claim 1, wherein at least one of the gliding surfaces has asloped surface and/or a surface which is convex relative to the lockingpart.
 9. The manual machine tool according to claim 1, wherein bothgliding surfaces adjacent to the vertex are at an angle and/or have anincline in the direction of the locking indentations.
 10. The manualmachine tool according to claim 1, wherein at least one of the glidingsurfaces has an incline of at least 12°, or at least 25° or 30° from thevertex to the locking indentation adjacent to the vertex.
 11. The manualmachine tool according to claim 1, wherein a gliding surface along whichthe locking part glides in the event of a relative movement of thelocking structure and the locking part has a lower incline than agliding surface along which the locking part glides in the event of alinear adjustment of the locking structure and the locking part relativeto one another.
 12. The manual machine tool according to claim 1,wherein the locking part has a convex curved and/or spherical glidingsurface to glide along the locking structure.
 13. The manual machinetool according to claim 1, wherein the locking part has a glidingsurface with a gliding coating to glide along the locking structure. 14.The manual machine tool according to claim 1, wherein the locking partis spring loaded by means of at least one spring into a locking positionwhich engages in the locking indentations.
 15. The manual machine toolaccording to claim 14, whereinc the locking part is deflected by thespring loading from the unstable position on the vertex into one of thelocking indentations adjacent to the vertex.
 16. The manual machine toolaccording to claim 1, wherein at least one spring arrangement isarranged between the actuating part and the at least one switching gearelement.
 17. The manual machine tool according to claim 16, wherein thespring arrangement between the switching gear element and the actuatingpart is provided by the coupling element.
 18. The manual machine toolaccording to claim 1, wherein the coupling element is or comprises aspring element and/or whereinin the coupling element is a spring bow orcomprises a spring bow, wherein the spring bow is extended in aring-shaped manner about the at least one switching gear element. 19.The manual machine tool according to claim 1, wherein the actuating partis pivotably mounted about an actuating pivot axis relative to themachine housing of the manual machine tool and/or is displaceablymounted about a linear actuating longitudinal axis.
 20. The manualmachine tool according to claim 1, wherein a deflecting gear is arrangedbetween the actuating part and the at least one switching gear elementto deflect a pivot movement of the actuating part into a linear movementof the at least one switching gear element or to deflect a linearmovement of the actuating part into a pivot movement of the at least oneswitching gear element.
 21. The manual machine tool according to claim1, wherein the actuating part has an arch-shaped or barrel-shaped walldesign and/or wherein the locking structure is arranged on the actuatingpart.
 22. The manual machine tool according to claim 1, wherein agliding coating is provided on the at least one vertex and/or on atleast one gliding surface and/or the locking structure has a smallerfriction coefficient on the vertex and/or on at least on gliding surfacethan in the region of at least one of the at least two lockingindentations.
 23. The manual machine tool according to claim 1, whereinthe switching gear element comprises a first switching gear element andat least a second switching gear element which can be adjusted in alinear manner in each case by means of the actuating device between afirst setting position and a second setting position relative to agearbox housing, wherein the first switching gear element can beadjusted in a linear manner by the deflecting gear along its pivot axisby means of a pivot movement of the actuating part about the actuatingpivot axis.
 24. The manual machine tool according to claim 23, whereinthe deflecting gear comprises a carrier ring which extends in aring-shaped manner around the gearbox housing and is rotatably mountedabout the actuating pivot axis, which carrier ring is coupled to thefirst switching gear element by means of a first coupling element tocarry out the linear adjustment of the switching gear element, and inthat the actuating part is mounted in a manner which permits the lineardisplacement on the carrier ring along the actuating longitudinal axisand is coupled to the at least one second switching gear element bymeans of a second coupling element to enable the linear displacement ofthe second switching gear element.